Calculating machine



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GALCULATING MACHINE Filed May a.' 1954 12 Sheets-Sheet 5 umm MQ wNN ' INVENTOR.

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CALCULATING MACHINE Filed May 1954 l2 Sheets-Sheet 8 ANN MNR

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CALCULATING MACHINE Filed May 8, 1934 12 Sheets-Sheet 9 INVENTOR.

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. mama @MQ f@ INVENTOR. Cav/ /l/I. F. Fr/'aen TroRN Jan. 28, 1941.

c. M. F. FRIDE'N GLCULATING MACHINE Filed May 8, 1934 12 Sheets-Sheet 11 lmlnlll,

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CALCULATING MACHINE Filed may 8, 1934 12 sheets-sheet 12 Patented Jan. 28, 1941 v UNITED STATES PATENT OFFICE 1 CALCULATING MACHINE Carl M. F. Friden, Orinda, Calif., assigner to Friden Calculating Machine Co. Inc., Oakland, Calif., a, corporation of California Application May 8 1934, .Serial No. 724,482

4 claims. (01.235-62) My invention relates to calculating machines ly below the numeral whee1 centralizing strip 24|, andis especialy concerned withamachine for efand With the right hand portion of the View fecting the four rules of calculation. broken away to a level immediately below the The vobject ofJmy invention is, in general, 'to zero-resetting rack 246. 5 provide an improved calculating machine. Figure 3 is a fragmentary cross-sectional view 5 Another object of my invention is to provide thru the keyboard with the right-hand portion an improved calculating machine of the type havtaken immediately in front of cross plate |11, the ing a reversible accumulator 'and uni-directionalcentral portion taken in the plane of the line 3-3 ly operable actuating means. in Fig. 1, and the left-hand portion of the view is o A further object of my invention is to provide broken away to the rear plate |16 to show its con- 10 improved division mechanism for a calculating struction. Certainparts shown in section and machine, which consumes a minimum time for others omitted to illustrate various details of performing a division operation. construction of the keyboard.

A further object of my invention is to provide Figure 4 is an elevational section taken longituimproved division mechanism for` a. calculating dinally and vertically of the machine as indicated l5 machine, which employs a programmed operaby the line 4-4 in Fig. 1B. tion control and in which the cyclically operable Figure 5 is a, fragmentary view similar to Fig. 4, drive mechanism operates continuously without but with gear 62 and disc 84 removed to illustrate stopping from the beginning to the end of a divithe clutch construction. sion operation. Figure 6 is a plan view, partially in section, of 20 Another object of my invention is to provide in the main drive train and clutch of the machine, a calculating machine of the type having reversithev view being indicated by the line 6 6 in ble numeral wheels and uni-directionally opera- Fig. 7.

ble actuating means therefor, improved mecha- Figure 7 is an elevational section taken longinism for performing division operations. tudinally and vertically of the machine as indi- 25 Another object of my invention is to provide in cated by the line l-'l in Fig. 1B. acalculating machine of the type having reversi- Figure 8 is an elevational section taken longible numeral wheels and uni-directionally operatudinally and vertically of the machine as indible actuating means therefor, improved mechacated by the line 8-8 in Fig. 1B, and showing the nism for controlling the sign character of the major control keys and their associated mecha- 30 registration on the numeral wheels. nisms.

A further object of my invention is to provide Figure 9 is a rear elevational View, partly in improved actuator means for tlie revolutions section, of the upper part of the machine, showing counter of a calculating machine. the carriage shifting mechanism.

The foregoing and other objects are attaind Figure 10 is a vertical cross-sectional view of 35 in the embodiment of the invention shown in the a part of the carriage shifting mechanism taken drawings, in Whichin a plane indicated by the line Ill-I0 in Fig. k9.

Figure l is a longitudinal sectional view through Figure 11 is a horizontal cross-sectional view oi' one orderof the calculating machine as indicated a portion of the machine as indicated by the line by the line I-I in Fig. 1B, illustrating the rela- II-II in Fig. 8'. 40

tion of the keyboard to the accumulator and its Figure 12 is a sectional elevation of the machine actuating mechanism, as well as the Arevolutions on a vertical longitudinal plane indicated by the counter and its actuator. Certain of the parts line |2 2 in Fig. 1B.

are shown in elevation. Figure 13 is a. sectional elevation of the machine Figure 1A is a perspective elevational view of on a vertical longitudinal plane indicated by the 45 the calculating machine. line |3-I3 in Fig. 1B. u

Figure 1B is a plan view of the rear portion of Figure 14 is a sectional elevation looking tothe machine with the shiftable carriage removed Ward the rear of the machine with portions broken and with certain parts broken away and others away in successive steps from left to right in shown in outline to obtain clearness. each order shown. 50

Figure 1C is an enlarged sectional view corre- Figure 15 is a fragmentary view showing in` sponding to the rear portion of Fig. 1. longitudinal vertical section part of the carriage Figure 2 is a bottom plan view partially in secshifting mechanism as indicated by theiline |5-I 5 tion of the accumulator carriage, with the central in Fig. 1B. part of the view broken away to a level immediate- Figure 16 is a fragmentary view showing in 55 Actuatina and, selecting mechanisms The main shaft I3, at suitable intervals of its length, carries bevel gears 9| (Flgs. 1, 1B, 1C and 6) each of which meshes with a comparable bevel gear 92 fastened on its respective actuator shaft 93. The actuator shafts 93 are arranged in parallelism and are journaled in a pair of plates 94 and 96 extending transversely of the machine and in turn mounted in the frame plates 8 and 9. There are as many shafts 93 as there are orders in the particular machine.

Since the actuator shafts and their associated f mechanisms are duplicates, but one of them need be described as an illustration. The shaft 93 shown in Figs. 1 and 1C, for instance, in addition to the bevel gear 32 carries an actuator in the form of a segmental gear 91, illustrated in detail in Figs. 19 and 20. The periphery of the segmental gear 91 is provided. vwith two separate series 98 and 99 of teeth 0|. 'I'here are nine teeth in the complete series 99, the tooth shown at the upper portion of Fig. 19 being the shortest, while the three succeeding teeth ane each longer by equal increments, and the remaining ive teeth are all of the greatest axial length.

In the series 98 there are but ive teeth, the teeth being in line with the teeth in the series 89. However, the uppermost tooth in the series 98 is relatively short, while each of the four remaining teeth is longer than the tooth preceding it by an equal increment. While all of the actuators 91 are alike, they 'are arranged on their shafts 83 with alternate actuators displaced axially for clearance between successive ones, which are disposed in radial overlapping relation to reduce the width of the machine, furthermore, each of the actuators, as shown particularly in Fig. 14, is polarly displaced on its respective shaft 93 with regard to the remainder of the actuators in the group.

In order that the actuators 91 may be properly effective in the operation of the machine, I provide means to make each of the actuators effective upon an associated shaft |06 (Figs. 1, 1B, 1C and 20) which preferably is of square section except at opposite ends where it is journaled. The shaft |06 is `lournaled in the plate 94 and likewise in a plate |01 which is at opposite ends turned to provide brackets |08 fastened to the end plates 8 and 9 of the machine. Intermediate its ends the shaft |06 is likewise journaled in a cross wall |09 mounted in the end plates 8 and 9. The shafts |06 are arranged in parallelism, not only with each other but likewise with their respective actuator shafts 93.

For each of the actuators 91 I preferably provide two actuated pinions and ||2 (Figs. 1, 1B, 1C, 19 and 20). Each of the pinions is provided with ten teeth cut to mesh with the teeth ||l|. The pinion is designed to cooperatel with the series 98, While the pinion ||2 is designed .to co-operate with the series 99. To this end the pinions and ||2 are axially slidable on the squared shaft |06. In order to control `the momentary position of each of these pinions and to translate the pinions along the shaft when desired, I extend each of thepinions to provide a collar ||3 and IM, leaving an intermediate groove such as ||6 and ||1.

The means for moving the two pinions and ||2 are quite similar. A cam plate |2| (Figs. l, 3 and 14) is mounted on a pair of links |22 and |23 by pivotal connections |24 and |26 respectively. 'I'he link |22 at its lower end is journaled on a'rod |21 which extends transversely of the machine and is held between an angle strut |28 anda strap |29 which is struck up from held between the frame plates 8 and9 and a strap |33 struck up from the. material of the angle bar |32. This method of mounting p'ermits a motion of the. plate |2| which is virtually a translation in a. longitudinal direction.

In order that the plate |2| may'likewise be guided from the lateral aspect and in a rectilinear path, I arrange that the cross plate 94 (Figs. l and 14) is cut with suitable slots |36, while a comparable plate |31 arranged adjacent the other end of the cam plate |2| is likewise along its upper edge cut with suitable slots |38. Furthermore, in order that the plate |2| will be urged'toward one extreme position, I preferably extend the link |23 to provideva hook |39 on which is fastened one end of a coil spring |4|, the other end of which is connected to a bracket |42 running transversely of the machine and held between the frame plates 8 and 9.

In this described fashion the cam plate |2| (Fig. 1) is conned to substantially a rectilinear path of travel and is urged in a direction by the spring |4| such that an extension |43 which at its extremity is looped to lie within the groove I1, is effective to translate the pinion I2 axially of the shaft |06 and out of the path of rotation of the tooth series 99 on the actuator 91. Movement of the cam plate |2| against the urgency of the spring IM, however, is effective to translate the pinion 2 on the shaft |06 into the path of the tooth series 99. The amount of vtranslation of the pinion ||2 is determinative of the number of teeth on the actuator which will be effective to gear with the teeth of the pinion and, consequently, is determinative of the amount of polar or angular rotation of the shaft |06 for each rotation of the actuator 91.

That is to say, if the pinion ||2 is in the position shown in Fig. 1C, none of the teeth in the series 99 is effective upon the pinion 2, and the shaft |06 is not rotated by any of the teeth of the series 99. However, if the pinion 2 is axially translated to lie within the path of the longest teeth of the series 99, then, since there are six equally long teeth, six of the teeth of the pinion ||2 are engaged thereby and the shaft' |06 is rotated six units for the ten units making up one complete rotation of the shaft 93. Correspondingly, if the pinion ||2 is moved to engage `the next shorter teeth,`of which there are seven in the series 99, then the shaft |06 is rotated seven-tenths of a rotation for each complete rotation of the shaft 93. Correspondingly, if the pinion 2 is moved to mesh with the shortest teeth of the series'99, then, since there are nine of such teeth, the pinion 2 will be rotate'd through nine-tenths of a complete rotation -for each rotation of the actuator 92.

A quite similar mechanism is elfectiveupon the pinion That is, if this pinion ,is moved axially into the position shown in Fig. 1C, it meshes with none of the teeth on the actuator 91. However, if the pinion is translated to mesh with the longest tooth of the series 91, then, since there is but one such tooth, the pinion l|| rotates the shaft |06 for but one-tenth of a rotation for each complete rotation of the actunally, if the pinion should be axially translated to lie in the path of the shortest teeth in the series 98, then, since there are five of such teeth, the pinion will be meshed therewith to rotate through five-tenths of a complete rotationl for each single rotation of the actuator 91.

The pinion (Figs. 1 and 14) is axially translated by means of an extension |51 which is hooked to lie within the groove M6 and is part of a cam plate |52 mounted by links entirely comparable to the described links |22 and |23 and guided between the plates |31 and 54, The dierence between the cam plates |21 and 52 is simply that the cam plate 12d is provided with four cam contours E53, |54, |55 and '|5'6, each of a different and progressively increasing slope, while the cam plate |52 is provided with ve cam contours 151, H56, |55, |613 and |5|, each one of a progressively increasing slope.

Keyboard The cam plates |121 and |152 (Figs. 1 and 3) of each pair which is provided inthe keyboard or selector mechanism for each order, are arranged to lie on opposite sides of the plane of a series or bank of keys, generally designated |66, which project through the upper portion of the machine (Fig. 1A) for convenient manual operation. The keys are all virtually identical, so that a description of one will serve as an example of all. Each key 61 (Figs. 1, 1C and 3), for example, is a relatively at plate which intermediate its ends is provided with a -pair of elongated slots |68 and |59. The slots ride over transverse through-rods |1|| and |12 respectively, which are carried for each bank of keys by a pair-of spacing channels |13 and |15. 'I'he pairs of channels in turn at their opposite ends are carried in perforated master plates |16 and |11 which are suitably flanged and secured to the end plates 8 and 9 of the'machine. Each key |61 at its upper end is provided with a finger cap |19, so that the key can be suitably translated on the rods |1| and i12.

Although the key can be digitally depressed, it must bevreturned to elevated position by a spring, which, in the present case, is for each bank of keys a sinuously arranged coil spring |82 anchored at opposite ends in the plates |16 and |11, and between its ends passing over the successive rods |1|, and between such rods passing under a pin |83 projecting laterally from an ear |84 forming part of the key |61. Depression of the key |61 and, correspondingly, of the pin |183 causes the spring y|82 between successive ones of the rods |1| to elongate, so that when the key |61 is released the force of the spring tending to contract or straighten itself causes the key to return to uppermost position, as indicated in Fig. 1.

Thel keys which represent the numerals from 1 to 5, at their lower ends carry transverse pins |86 which project in a direction to co-operate with the cam faces |51 to |6|, inclusive, of the cam plate |52. For instance, depression of the key |61, representing the numeral 1, is effective' to cause the pin |86 of such key to ride over the cam face |51 and approximately to translate the lcam plate |52 a single unit amount, thus pulling the pinion into the path of the single, longest tooth of series 98 on the actuator 91. Thus, when the actuator rotates through a single cycle, the longest tooth of the series 98 will gear with the teeth of the pinion and will cause one-tenth of a rotation of the shaft |06 for the complete cycle of rotation of the actuator 91. correspondingly, the key representing the number 2 has a pin |86 at its lower end which meshes with the cam face |58. The inclination of this cam face is such that when the key representing the numeral"2" is depressed the cam plate |52 is translated through two units of motion, thus causing the two-tenths position of the pinion to be assumed. The same considerations `apply to the key representing the numeral 3 which moves the cam plate |52 through three units, for the key representing the numeral 4 which moves the cam plate |52 through four units of motion, and for the key representing the numeral 5" which in engaging the cam face |6| moves the cam plate 52 through five units oi motion.

Similarly the key representing the numeral 6," when depressed, engages the cam face |53 to translate the cam plate |21 and to move axially the pinion ||2 into the path of the longest teeth of the series 99, which produces six-tenths of a rotation of the shaft 156 for each rotation of the actuator 91 Correspondingly, the key representing the numeral 7 engages the cam face |54 on the cam plate i2! and causes translation of the pinion ||2 into that portion of the path of the series 99 which will produce an appropriate rotation of `the shaft |06.

In the same fashion the key representing the numeral 8 when it engages the cam face |55, and the key representing the numeral 9 when it engages the cam face |56, are eiective to produce a proportionate number of unit translations of the cam plate |2| and produce an appropriatie and corresponding orientation of the pinion 2.

In order that each of the keys |61 will be held in its depressed position, I provide each of the keys |61 (Figs. 1 and 3) with a suitable notch 20| which, when the key is fully depressed, is adapted to be entered by a sliding plate 202 extending along the bank of keys and having therein a plurality of apertures 203, one for each of the keys of the bank. The plate 202 at opposite ends is carried by the strips |16 and 11, but projects as at 204 from the strip |11 and is bent to form a seat for a coil spring 206 which likewise abuts the member |11. The plate 202 is therefore urged into a position in which it will interengage with the notch 20| to lock in position the particular key of the bank or order which is depressed. Movement of the plate to the right in Fig. l, however, releases the depressed key. In order to move the plate to releasing position against the urgency of the spring 206, each of the keys is likewise provided with a notch 201 having an inclined upper boundary, so .that the initial movement of the key toward depressed position rst moves the plate 202 to key-releasing positionso that any key which prior thereto has been latched in depressed position will be released.

The key |61 (Fig. 1) of each bank which represents Ithe numeral 0 is in the main like the remaining keys in that it is translated on rods |1| and |12. However, instead of engaging the spring |82 it is provided with an extension 2| which engages a Ycoil spring 2|2 mounted on a projection 2|3 on the plate |11., This spring normally urges the key upwardly. Furthermore, this key is not provided with any means for locking it or holding it in depressed position. and on the other hand is provided with an exaggerated inclined surface 2|4 for moving the plate 232 to releasing position. Thus, as a matter of fact, the key |61 representing the numeral "0 acts as a clear key for its own bank or order.

With the selector or keyboard described it is possible, therefore, to so orient the pinions and ||2 that the shafts |03 will be rotated an amount equivalent to any particular number or value desired to be introduced into the several orders.

Plus-minus mechanism vIn order that the numeral wheel 234 (Fig. 1) will indicate an appropriate and corresponding i rotation of the shaft |06, I provide on the shaft Y |36, between the cross plates |03 and |01, a shiftable spool 26| at one end carrying a. ten-tooth gear 262 and at the other end carrying a tentooth gear 263. In the neutral position shown in Fig. 1; neither of these gears is in mesh with a ten-tooth gear 264 which is fast on th numeral wheel shaft 233. On the other hand, when the spool 26| is shifted to the right, 'as seen in Fig. 1, the gears 262 and 264y are in mesh, while when the spool 26| is shifted to the left, as seen in Fig. 1, the gears 263 and 264 are in mesh. By this Yarrangement the shaft 233 can be connected to the shaft |06 to partake always of a movement which is proportionate thereto but Ithe direction of which is dependent upon which of the gears 262 or 263 is utilized. Thus, while the shaft |06 always operates in a predetermined direction and never reverses, nevlertheless the shaft 233 can be rotated either in a positive or additive direction. or, alternatively, in ,a negative or subtractive direction.

Accumulator The machine of my invention includes a carriage 226 (Figs. 1, lA, 1C, 4 and 8) 'containing a register or accumulator, generally designated 221, the individual orders of which can be aligned with the desired individual orders of the selector and actuator mechanisms lby translation of the carriage transversely of the machine. 'Ihe carriage is provided with runners 228 and 229, respectively, the latter of which engages with a suitable track 23| forming part of the framework of the machine, and the former of which runs on an extension of the transverse plate |01. Within the carriage, which is'essentially a hollow casing, there is provided a main support 232 (Figs. 1 and 2) which extends transversely of the carriage and at ysuita-ble intervals carries a plurality of numeral wheel shafts 233. Since each of the numeral wheel shafts is identical with its fellows, -but one need be detailed for descriptive purposes.

The shaft 233 (Figs. 1, 1C and 2) is journaled between its ends not only in the support 232 but likewise in the carriage frame 226, and carries at its upper end a generally conical numeral .wheel 234 the individual numerals of which, from 0 to "9," inclusive, are individually observable through anvinspection aperture 236 (Fig. 1A) in the carriage shell. A guide bar 231 (Figs. 1C and 2) mounted exteriorly of the carriage carries slides 236 which can be arranged as desired to demark groups of the apertures 236. In order that the individual ones of the numerals on the wheels v234 will be properly aligned with the viewing aperture 236, I preferably mount adjacent the 5 trlcally with the shaft 233 'with a star-shaped aperture 242 providing ten successive depressions. Projecting from 'the shaft 233 is a spring-pressed ball 243 adapted to ride in the successive depressions 242. Since these depressions are aligned with the respective numerals on the wheel 234, the shaft 233 is resiliently urged to centralize 1tself in any one of ten positions, but in each of such positions one of the numerals on the wheel 234 iszii precise alignment with the viewing aperture Accumulator vzero resetting mechanism Since, duringthe operation of the machine, the

numeral wheels 234 are left in variously oriented positions, and since it is further desirable to return each of these wheels to a given initial or zero position, I provide a clearing means for rotating the individual shafts 233 a suflicient amount to restore simultaneously all of the numeral wheels 234 to zero position. Each of the shafts carries for this purpose a mutilated pinion 244 (Figs. 1, 1C and 2). This was originally a ten-tooth pinion but it has had one tooth removed to make it a nine-tooth pinion with an interrupted zone. In order to conserve space, alternate ones of the shafts 233 have the pinions 244 located at different axial positions thereon.

The alternate pinions 244 ail mesh with a multi-sectional rack 246 which is constrained to move in a rectilinear path by a pair of projecting screws 241 operating in elongated slots 248 in the support 232. At intervals equal .to the distance be-` l tween alternate ones of the wheels 244, the rack is cut away', as at 243, to provide individual racks, each of which is normally out oi mesh with the adjacent one of the pinions 244. 'I'he intermediate pinions 244 are comparably arranged for en.

However, when the rack 246 is translated, say, 1:0-,

ward the right in Fig. 2 by means of a knob 252 which projects from the casing 226, then the rack teeth engage with the teeth of the interrupted gears.244 and rotate each of the gears, if they are already out of zero position, a sufl'lcient amount until the interruptions are in the position shown in Fig. 2 in which the numeral wheels v234 are in zero position and the entire register is clear. The rack 246 is returned to the position shown in Fig. 2 by means of a suitable spring (not shown). The return movement is ineffective upon the shafts 233 inasmuch as there is no intermeshing between the rack and the pinions When the pinions are in zero position. 'I'he shafts 233 are therefore easily restorable to zero upon manipulation of the handle 252,' and are properly centralized in any position lby the members 243.

Accumulator tens transfer mechanism But, for either direction of rotation of a. shaft 233, for each complete rotation thereof the corresponding shaft 233 of the next higher order support 232 a strip 24| which is pierced concenshould partake of one-tenth of' a complete rota- 75 tion in the same sense. In otherwords, a tenscarrying mechanism between the successive shafts 233 must be provided.

To this end the shaft 233, between the tentooth gear 264 and the lower leg of the support 232, carries, particularly as shown in Fig. 2, a one-tooth gear 266. Journaled in the lower leg ofthe support 232 as well as in a strap 261 mounted parallel thereto, 'is a shaft 268 (Figs. 2 and 22) which carries a bell crank 269. One arm 21| of the bell crank carries a single tooth 212, while the other arm 213 carries a projecting pin 214 which extends laterally into the region of the next successive order. Thus, for a single rotation of the shaft 233 the one-tooth gear 266 operates the bell crank' 269v a single time. When the teeth 266 and 212 are not in opposition the pin 214 is retracted, as shown in Figs. 1 and 2. However, when these teeth come into opposition at the tens-carrying position of the shaft 233, the pin 214 is projected and translates a quill 216 (Figs. 1, 14 and 22) which is slidable on the squared shaft |06.

The quill at one end carries a disc 211 which runs between a fork 218 forming part of a slide 219 working in suitable slots in the members 96 and |01. The slide 219 at its opposite end is provided with a pair of notches 28| (Fig. 1C) and 282 respectively, either of which is adapted to seat on a through-rod 283 extending transversely of the machine and carried in a bracket 294i projecting fromthe plate 191. A coil spring 286 at one end is in engagement with the slide 219 and at the other end is hooked to a projection 281 on the plate H81. The slide 219 is held by the spring 286 with one or the other of the notches 28| or 282 in engagement with the rod 283 which therefore acts as a centralizer for either of the two extreme positions of the slide 219.

When, therefore, the pin 214 is projected, due to the initiation of a tens-carrying operation, the disc 211 is translated toward the left in Fig. 1 and moves the slide 219 with it. The disc assumes its other extreme position, being centralized therein since the notch 282 is in engagement with the rod 283. The quill 216, in addition to the disc 211, carries a ten-tooth gear 288 (Figs. 1, 1C and 22) which, when the quill is translated, to the left in Fig. 1, on the shaft |96, moves into the path of a single-tooth gear or actuator 289 on the actuator shaft 93 located between the members |09 and 96. Since the lever arm 213 extends from the lower order toward the higher order, the tens-carrying actuator289 on the shaft 93 isV eiective to rotate the shaft |06 through one-tenth of a rotation to complete the tens-A carrying operation in the next higher order.

Since the tens-carrying actuator 289 lspower driven, it is desirable to have a centralizing mechanism on the shaft |06 which will be effective to hold the shaft |06centralized, not only after rotation thereof by the actuator 91 but also afterv rotation thereof by the tens-carrying actuator 289. For this reason-there is mounted on the shaft |06 a Geneva wheel 29| (Figs. 1, 14 and 20) having ten concave faces. These faces can each mate with a disc 292 mounted on the shaft 93. 293 (Fig. 20) and a notch 294. When the cutaway portion 293 is adjacent the Geneva wheel 29|, the shaft |06 is freeto rotate, except for the centralizing action. of a star-wheel 296 (Figs. 1

`andI 14) against which operates a detent lever 291.

All of the detent levers 291 are urged into position by a sinuous spring 298 threaded be- The disc 292 has a cut-away portion.

tween successive pairs of pins 299 and 300. The shaft |06 can rotate under the superior urgency of the actuator 91, but at the conclusion of suchy intergeared rotation the Geneva wheel 29| is again held in position by the disc 292 which appropriately rotated along with the actuator shaft 93. But in addition to freeing the shaft |66 when it is to be rotated by the actuator 91, the disc is so oriented that the notch 294 comes into jux taposition with the Geneva wheel 29| at an appropriate time to permit the actuation of the shaft |66 by the tens-carrying actuator 289.

Means for restoring the tens-carrying mechanism to its inactive position include a singletooth actuator 269 (Figs. 1 and 22) provided with an axially cammed extension 30| which, as soon as the ten-tooth gear 288 has 'been advanced onetenth of a rotation and the single-tooth actuator 289 has come out of mesh therewith, is effective.

Revolutions counter mecham'sm Mounted on the carriage 226, in. addition to the accumulator, is a revolutions counter, generally designated 306 (Fig. 1). This register comprises a plurality of shafts 381 journaled at opposite ends in extensions308 and 809 ofthe carriage frame 229. The spacing of the shafts 301 is the same as the spacing of the successive orders in the multiple register. Each of these shafts 301 carries a numeral wheel 9H bearing numerals from 0 to 9 inclusive, spaced apart on the periphery of the wheel and adapted to be seen through a reading aperture 3|2 cut in the upper face of the carriage shell 226.

The individual numbers of the wheel 3H are properly centralized in line with the aperture 312 by a centralizing mechanism 913 similar to aperture 242 and ball 248, shown in Fig. 2. Also, the shafts 301 are alternately provided with axially offset clearing gears 3|4 meshing with a multisectional clearing rack 8|6 in exactlythe same fashion as the rack 246 and the. gears 29d. The rack 303, however, is operated against the urgency of a suitable spring (not shown) by means 3|| arranged in spaced relationship and in any desired number for the capacity of the machine. The individual wheels of .this register are all properly centralized and can simultaneously be restored to zero or cleared position by operation of the knob 3|8 (Fig. 1A). Furthermore, one or more markers 3|9 slidably mounted on a strap 320 are available forrdemarking groups of the numeral wheels 3| i.

In order suitably to actuate or introduce values into the revolutions counter there is provided a suitable actuator. The actuator includes a member 32| (Figs. 1C, 18, 23 and 24) which has a compound motion having two major components, one a translatory reciprocation and the other a. rotary oscillation. 'Ihat is. the member or shaft 32| is mounted in the plates 8 and 9 to move from end to end and to be rocked back and forth. Mounted on the shaft is a pair of collars 322 each of which is extendedto support a pair of parallel rods 323 andA 324. Disposed on the shaft 32| between the rods 323 and 324 is a plurality of actuator spools 326 which in general are identical and are of such size as to be spaced with the same spacing as the shafts 301, all of the spools except the right hand one in Fig. 18 being operative for transfer actuation only, while the right 'hand spool 326,carries the counting actuator. The right hand spool 326 as viewed in Fig. 18 is only partially complete as compared with the other spools, and carries a finger 321 which projects radially between a tentooth gear 328 (Fig. 1) and a single-notch disc 329 (Figs. 1C and 24) both on the shaft 301.

Forming part of the finger 321 is an eyelet 33| to which is hooked a spring 332, the other end of which is hooked on the rod 323. Thus, the spring 332 urges the finger 321 to rotate clockwise, as seen in Figs. l and 1C, about the shaft 32|. Such movement of the finger, however, is restrained by a projection 333 likewise forming part of the spool 326 and engaging with the shaft 324. As particularly seen in Figs. 1 and 1C, therefore, as the shaft 32| rotates or oscillates clockwise, carrying with it the frame rods 323 and 324, under the urgency of the spring 332 the finger 321 is moved to introduce itself between successive teeth on the gear 328. At this juncture the rotary oscillation of the shaft 32| is interrupted and the shaft is translated axially toward the right, as seen in Fig. 18, for instance. Such movement, since the finger 321 remains intermediate successive teeth on the ten-tooth gear 328, is effective to rotate the shaft 301 for onetenth of a complete revolution, and thus to advance the numeral wheel 3|| for one successive digit.

At the conclusion of such axial movement toward the right, as seen in Fig. 18, for instance, the shaft 32| again oscillates, but this time in an anti-clockwise direction, so that the finger 321 is rotated positively, due to the contact of the shaft 324 against the finger 333, into the position as seen in Figs. 1 and 1C in which the finger is out of mesh with the pinion 328. The return axial movement of the shaft 32| toward the left, as seen in Fig. 18, therefore, restores the parts to their original position. By the described operation, the numeral wheel 3II is advanced one unit, with the numerals properly aligned with the inspection aperture by the centralizing mechanism 3|3.

It is especially pointed out that if, when the shaft 32| initially rotates to mesh the finger 321 with the ten-tooth gear 328, such meshing movement is followed by an axial translation of the shaft 32| toward the right, for instance, in Fig. 18, then the numeral wheel is advanced in a positive direction. On the other hand, if, following the initial meshing movement of the finger 321 with the gearv 328, the axial translation of the shaft 32| is toward the left, as seen in Fig. 18, then the direction of movement of the shaft 301 and the numeral wheel 3|| is subtractive or negative.

' Tens transfer mechanism for the revolutions counter To this end the spool 326 which is arranged in' termediate the lowest order and the next higher order, as seen inv Fig. 18, is not only provided at its left-hand end with a finger 321, but is also provided at its right-hand end with a finger 336 which is bent to be co-planar with finger 321 of lowest order and carries a projection 331 so that the parts are in contact when they bear the relationship illustrated in Figs. 1C and 23. Thus, the spring 332 of the tens order, for instance, as seen in Fig. 18, is effective to urge the finger 336, and particularly its projection 331, into contact with the finger 321.01' the units order. However, the spool 326 of the units order cannot yield because its projection 333 is in contact with the shaft 324. When,

. however, the shaft 324 rotates about the axis of the shaft 32|, the finger 336, under the urgency of its spring 332, tends to follow the finger 321,V but can only do so when the notch (Fig. 24) in the disc 329 of the units order is in position therefor, which only occurs when the units order counter numeral wheel passes from "9 to 0 and vice ve If the notch is out of passingposition, i. e. when no tens carry has been determined by the units order counter numeral wheel, the finger 336 cannot pass by the barrier of the disc, then the spool 326 cannot rotate about the axis of the shaft 32| and finger 321 of the tens order is held in inactive position. Correspondingly due to the similar interlocking relationship of the remainder of the spools 326 for the higher orders, all such higher order spools are maintained stationary. But on the other hand, if the tenscarrying notch in the disc 329 of the units order, for example, is in position to permit passage of the finger 336 associated therewith, then such finger rotates along with the finger 321 of the units order and causes a corresponding rotation of the spool 326, and the finger 321 of the tens order is effective on the gear 3| 4 and the shaft 301 of the next higher or tens order in the revolutions counter to rotate such shaft through one-tenth of a rotation and thereby effect the tens-carrying operation.

Operation of revolutions counter actuator The rotary oscillation of the shaft 32| is produced in synchronism with the rotation of the shaft 83. At the end of the shaft-83 which projects through the frame plate 8 there is mounted an eccentric 34| (Fig. 13) against which bears a. follower 342 projecting from one arm 343 cf a bell crank generally designated 344 and pivoted as at 346 on the plate 8. A coil spring 341 is anchored to the plate 8 at one end by a pin 348 and at the other end is connected to a pin 349 on the arm 343. 'I'he bell crank is likewise provided with an arm 35| which is forked to engage a pin 352 on a crank 353 mounted on the opposite side of the plate 8 and fastened on the shaft 32|. The pin. 352 projects through an aperture 354. Thus, for each complete rotation of the shaft 83 the bell crank 344 is oscill-ated about the pivot 346 and through the crank 353 causes a comparable complete oscillation of the shaft 32|. The timing of the rotary. oscillation provides for 'engagement of the actuator finger 321 with thevassociated gear 328 by the first half or phase of such rotary oscillation which occurs during the first part of the cycle, then a dwell occurs in such rotary oscillation While the engagement of the nger and gear is maintained to allow the first half or phase of the axial translation to cause movement of the gear translation to return the actuator finger toits starting position.

The longitudinal cr axial translation of the shaft 32| is provided by a mechanism especially illustrated in Figs. 6 and 7. On the shaft 83 is mounted a cam drum 358 having a pair of grooves 351 and 358 cut therein. These cam or angularly grooves are of identical contour but are polarly spaced from each other.v In order to change the phase relationship of the axial movement of -the shaft 32| to the rotary movement thereof, I provide means for optionally engaging either o f the grooves 351 and 358.

To this end, on the frame plate 9 I provideA a pair of projecting ears 36| and 362. These ears mount a cross-shaft 363 which is held in place by suitable pins 364 and on which is mounted a sleeve 366. The lower end of the sleeve is united to a lever arm 311 at the extremity of which is a follower pin 318. Likewise on the sleeve 366 is a lever arm 318 at the extremity of which is a follower pin 38| adapted to extend into the groove 3511.

4To hold the sleeve 366 in either desired extreme position, I likewise provide on the sleeve a groove 382 in which runs a shifting pin 383 projecting through an aperture 384 in the plate 9 and carried at the end of a lever 388 fast on a shaft 381|. Thus, as the shaft 381i is rotated between its two'extreme positions, the pin 383 `shifts the sleeve 366 along the shaft 363. In thi-s fashion, either the pin 318 is introduced into the groove 358 so that the sleeve 366 reciprocates in phase relationship with the characteristics of the groove sleeve 366 is shifted in the opposite direction or Y downwardly on the shaft 263 and the pin 388 isA engaged in the groove 361 so that the sleeve in such circumstances partakes of the reciprocatory movement imparted by the cam groove 351..

The motion of the sleeve 366, which is a rotary oscillation, is transmitted by a lever arm 386 which is fixed to the sleeve and at its extremity is forked, particularly as shown in Figs. 6 and 18, to engage a. radially depending pin 389 projecting from the collar-322 encompassing the shaft 32|. If pin 318 is engaged with groove 358, the .first half of the axial reciprocation, which occurs during the dwell in the rotary oscillation of actuator finger 321, moves the finger to the left as viewed from the front of the -machine so that a negative registration is effected. After this first half of the axial reciprocation, a dwell occurs in such reciprocation to allow the second half or phase of the rotary oscillation which disengages finger 321 from the 'associated gear 328.A Aftersuch disengagement, the second half or phase o'f the axial reciprocation returns finger 321 to its initial position which it reaches substantially at theend of the cycle. If pin 38| is engaged with groove 351, the first half or phase of the axial reciprocation is a movement of iinger 321 to the right so that a positive registration is eiiected. Thus, as the main shaft 83 rotates it imparts to the shaft 32| an axial translation in either selected one of two different phase relationships with the driving shaft. The phase relationship which is selected in a particular instance con- 358, or, conversely, the

annessa trols the sign character of the registration on the numeral wheels 3|| in the revolutions counter, as outlined hereinabove.

Plus and minus keys Each strip is therefore guided in a rectilinear path. Adjacent the lower end, each key is provided with a projection 408 passing through a suitable aperture 408 in the control plate 54 and engaging with a coil spring 4|| which at its opposite end is anchored to a pin 4|2 on the control plate for urging the respective key to its uppermost position.

Depression of the plus key 40|, therefore, tensions the appropriate spring -4|| and likewise causes depression of a pin 4|3 projecting from the key and adapted to contact with an inclined cam face 4| 4 forming part of a slide 4|6 having elongated apertures H1 therein for allowing translatory movement of the slide on the supporting pins 401. The slide 4|8, as the key 48E is depressed, therefore moves correspondingly, being translated toward the left in Fig. 8. Between its endsthe slide 4I6 is provided with an aperture 4|'8 into which projects a pin 4|9 which passes through the control plate 54. 'I'he pin M9 is at one extremity of a lever 42| (Fig. 4) pivoted as at 422 on the frame plate 9, and in turn at its opposite extremity provided with a -fork 423 to engage a pin 428 at the extremity of a lever 426. This latter lever is pivoted by a headed bolt 421 on the control plate 64 and at its opposite end carries a pin 428 which extends through an aperture in the frame plate 9 and abuts one of the resilient arms-429 of the master switch generally designated 43|. This switch comprises, in addition to the arm 429, a resilient arm 432 which, with the arm 429, is suitably fastened to a pair of brackets 433 and connected to the conductors 44 and 45, respectively. Likewise carried by the resilient arms 429 and 432 are contactpoints 434 and 436, respectively.

Thus, when the slide 4|6 is translated toward the left, in Fig. 8, by the depression of the plus -key 40|, the pin 4|9 causes an oscillation of the lever 42|v (Fig. 4) about the pivot 422. This, due to the connection between the fork 423 and the pin 424, causes a corresponding oscillation of the lever 426 about its pivot point 421. Thus, the pin 428 urges the resilient contact lever 429 into lsuch a position that the contact 434 abuts the contact 436. The circuit is therefore closed through the electric motor 3| which is energized to drive the entrained mechanism.

Substantially simultaneously with the energizati'on of the motor, the clutch lever 16 is actuated. For this purpose the slide 4|6 (Fig. 8) likewise carries an elongated aperture 431 into which projects the pip 82 (Fig. 4) which is mounted, as heretofore described, on the clutchoperating lever 16. Upon the depression of the plus key 48| therefore, not only is the motor energiz'ed but likewise the clutch lever 16 is rocked so that `pawl 61 is engaged'with the ratchet 66, 

